EP2452078B1 - Dispositif constituant une restriction variable pour un écoulement fluidique - Google Patents

Dispositif constituant une restriction variable pour un écoulement fluidique Download PDF

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Publication number
EP2452078B1
EP2452078B1 EP09775737.1A EP09775737A EP2452078B1 EP 2452078 B1 EP2452078 B1 EP 2452078B1 EP 09775737 A EP09775737 A EP 09775737A EP 2452078 B1 EP2452078 B1 EP 2452078B1
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EP
European Patent Office
Prior art keywords
throttle
arrangement
section
fluid
lift
Prior art date
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Application number
EP09775737.1A
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German (de)
English (en)
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EP2452078A1 (fr
Inventor
Eneko Goenechea
Josef ZÜRCHER
Silvan Thuerlemann
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Bucher Hydraulics AG
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Bucher Hydraulics AG
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Publication of EP2452078A1 publication Critical patent/EP2452078A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0426—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with fluid-operated pilot valves, i.e. multiple stage valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B1/00—Control systems of elevators in general
    • B66B1/24—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"

Definitions

  • the invention relates to a lift control valve, a hydraulic lift system with the lift control valve and a method for operating the lift system according to the preambles of the independent claims.
  • variable throttle cross sections for fluid flows therein are used, both for the regulation of pressures and / or flow rates as well as for their detection.
  • the change in the throttle cross-section is carried out either by external Verstelling by means of mechanical, hydraulic, pneumatic or electric actuators, eg control valves, or by the pressure, a pressure difference and / or a flow force of the guided in the arrangement fluid, such as pressure relief valves or check valves.
  • the latter arrangements have the advantage that a high operational reliability is achieved due to the relatively simple hydraulic / pneumatic coupling and the independence of auxiliary power.
  • the disadvantage here, however, that these arrangements are typically used only in a flow direction.
  • the lift control valve has an arrangement for providing a variable throttle area for a flow of fluid, preferably a fluid flow, e.g. a stream of hydraulic oil, on.
  • This arrangement includes a throttle assembly and a drive assembly.
  • the throttle arrangement forms a variable by movement of a throttle body throttle cross-section.
  • the drive arrangement has a drive element arranged movably in a housing, which is coupled to the throttle body of the throttle arrangement such that the throttle cross section of the throttle arrangement can be changed by changing the relative position of the drive element in the housing.
  • the coupling between the throttle body and the drive element takes place in a hydraulic or mechanical manner, advantageously by common, in particular one-piece construction of throttle body and drive element.
  • the arrangement is designed such that the drive element is permanently acted upon by a spring force (the claimed first spring force) or can be acted upon, for example by supplying auxiliary power, with such a spring force.
  • the spring force acts in a claim according to the first direction on the drive element, in which this in the housing is mobile.
  • a spring element or a pressurized compressible medium in a suitable direction exerts a compressive force directly on the drive element and / or on the throttle body coupled to the drive element.
  • the spring force causes the drive element is positioned in a basic position in the housing in the absence of at least equally large, acting in a direction opposite to the first direction claims according to the second direction on the drive element.
  • the arrangement is such that the drive element is fluidly in contact with a first side of the throttle cross-section or can be brought into fluidic contact with this first side due to fluid pressures in a first fluid space of the arrangement, and a second fluid space of the arrangement, which is permanently in fluidic contact with the other, second side of the throttle cross-section or can be brought into fluidic contact with this second side, with a second and a third force can be acted upon, both of which act in the second direction according to claim, ie against the spring force.
  • the arrangement is designed such that due to a fluid pressure in a third fluid space of the arrangement, the drive element is acted upon by acting in the claim first direction fourth force, ie with a fourth force acting in the direction of the spring force.
  • the arrangement comprises a switching arrangement, e.g. a hydraulically operable 3/2-way valve, by means of which either either the first and the third fluid chamber of the arrangement or the second and the third fluid chamber of the arrangement are fluidically connectable to each other.
  • a switching arrangement e.g. a hydraulically operable 3/2-way valve
  • the drive element is dependent on the switching state, i. depending on whether the third fluid space is connected to the first or the second fluid chamber, either on the occurrence of a positive or negative pressure difference between the first side and the second side of the throttle gap from the home position movable to open or enlarge the throttle cross-section.
  • an arrangement for providing a throttle cross-section for a fluid flow in which the throttle cross section is variable or openable depending on a pressure difference across this and in which the polarity of the pressure difference, by means of which the throttle cross section can be changed or opened is, is switchable.
  • the arrangement is designed such that the throttle cross section is completely closed when arranged in the basic position drive element, so the two sides of the throttle cross-section are separated from each other, so that in this position, the first fluid space from the second Fluid space is separated.
  • This separation is preferably carried out such that there is a leak-free separation at the intended pressures and the intended fluids.
  • the throttle arrangement is designed as a seat valve.
  • Such embodiments of the arrangement may be used, for example, as reversible check valves, which is a preferred use thereof.
  • the arrangement has means for determining the opening of the throttle cross section of the throttle arrangement, the relative position of the drive element in the housing and / or the relative position of the throttle body of the throttle arrangement, ie means with which a variable representing the respective throttle cross section can be determined.
  • these means comprise sensors with which the relative positions of the drive element and / or the throttle body can be converted into electrical signals, so that an electronic evaluation of the determined measured values is possible.
  • Such embodiments of the arrangement may e.g. be used as flow meter with reversible flow direction, which is a further preferred use of the arrangement.
  • non-compressible fluids e.g. Water or with only very low compressible fluids such.
  • Mineral oil has the advantage that, with known characteristics of the arrangement and known viscosity of the fluid all other required for the determination of the volume flow rates, that are the throttle cross-section, the hydraulic characteristic of the arrangement in this throttle cross-section and at the given viscosity of the fluid and the Pressure difference between the first and the second side of the throttle cross-section, with good accuracy from the determined, the throttle cross-section representing size result.
  • the arrangement is such that the second force and the third force are approximately equal at identical fluid pressures in the first and second fluid spaces, e.g. It can be achieved by directly applying force without over- or reduction mechanisms, the effective areas used to generate the respective force are made the same size. In this way it can be achieved that the operating behavior of the arrangement in both switching states, i. both when the first and third fluid spaces are interconnected via the switching arrangement and when the second and third fluid spaces are interconnected via the switching arrangement, apart from the reverse polarity, the pressure differential required to actuate the drive element is substantially identical.
  • the arrangement is designed such that at identical fluid pressures in the first, second and third fluid space, the second, third and fourth forces cancel each other substantially.
  • This can be achieved, for example, by the fact that, in the case of a direct introduction of force without over or reduction mechanisms, the active surfaces used to generate the second and third forces are of the same size as the active surface used to generate the fourth force.
  • a particularly sensitive response of the arrangement can be achieved, such that even slight pressure differences between the first and the second Side of the throttle cross-section lead to an opening or increase the throttle cross-section.
  • the drive element has axial surfaces which are fluidically connected to the first, the second and the third fluid chamber for generating the second, third and fourth forces, which is preferred, a direct and loss-free introduction of force into the drive element takes place.
  • the drive element of the drive arrangement and the throttle body of the throttle arrangement are formed by one and the same one-piece or multi-piece component. This allows a simple and compact design with a lossless coupling between the drive element and throttle body realize.
  • the inventive lift control valve has a first connection for a supply line for hydraulic fluid coming from a hydraulic pump, a second connection for a return of hydraulic fluid into a tank and a third connection for a hydraulic line leading to a hydraulic drive of a lift system.
  • the lift control valve has a control arrangement with which the first side of the throttle cross section and the first fluid space of the arrangement can be fluidly connected either to the first port or to the second port, depending on whether the lift control valve is to be brought into a position which is intended to allow the passage of hydraulic fluid from a hydraulic pump to a hydraulic drive of a lift system (OPEN-drive operation) or the return of hydraulic fluid from a hydraulic drive a lift system in a tank (AB-ride operation) when used as intended.
  • the lift control valve is configured such that the second side of the throttle cross-section and the second fluid space of the arrangement are connected to the third terminal or can be connected thereto.
  • the arrangement is incorporated into the main line through which the hydraulic fluid flows in the event of normal UP-drive operation and AB-drive operation of the lift control valve and, if designed accordingly, can be used, for example.
  • the system engineering effort compared to previous lift control valves can be significantly reduced with the same functionality and save corresponding provisioning and maintenance costs.
  • the lift control valve is designed in such a way that, when the first side of the throttle cross-section and the first fluid space are connected to the first port, the second fluid space will inevitably also be connected to the third fluid space by the changeover arrangement and Connecting the first side of the throttle cross-section and the first fluid space with the second port inevitably leads to the first fluid space is connected by the switching arrangement with the third fluid space.
  • control arrangement for enabling the selective connection of the first side of the throttle cross-section with either the first or the second port of the lift control valve is preferably provided steadily acting, preferably hydraulically actuated main valve used, which is preferably designed in piston valve design.
  • main valve used which is preferably designed in piston valve design.
  • the lift control valve has a valve with which the fluid supply to the hydraulic drive of the main valve on reaching or exceeding a certain pressure at the first port fluidly is connected to the second port, ie with the port which is provided for a return of hydraulic fluid in a tank.
  • control arrangement of the lift control valve has a hydraulically actuated main valve
  • the lift control valve has an electrically actuated pilot valve for the hydraulically actuated main valve
  • the hydraulic drive of the main valve fluidly with the second side of the throttle cross-section or connected to the third port or can be disconnected.
  • the fluidic connection between the pilot valve and the hydraulic drive of the main valve to the second port i. Having throttle leading to the tank connection.
  • This throttle point advantageously has a variable depending on the valve position of the main valve throttle cross-section.
  • the throttle cross section is variable in dependence on the position of the spool, which is advantageously realized such that the throttle cross section between the spool and a fixed component of the main valve is formed. As a result, a pressure relief of the connecting line between the pilot valve and the main valve is ensured with a closed pilot valve.
  • variable throttle cross section it is also possible to specifically influence the response of the main valve.
  • the lift control valve is designed in such a way that connection of the first side of the throttle cross section of the throttle arrangement to the second connection is not possible when hydraulic fluid is present under pressure at the first connection. In this way it can be ensured that an AB drive operation of a system formed with this lift control valve is possible only when the hydraulic pump or the hydraulic fluid flow is switched off.
  • the switching arrangement of the arrangement has a hydraulically actuable changeover valve, which is switchable during normal operation by opening or closing a pressure relief opening.
  • the control arrangement of the lift control valve is designed such that it when connecting the first side of the throttle cross-section of the throttle assembly with the second port (tank port) opens the pressure relief port of the switching valve.
  • the lift control valve is designed in such a way that the actuation energy of the hydraulic fluid guided in operation in the lift control valve can be removed for the actuation of hydraulically operated valves contained in it. In this way can be dispensed with further supply and discharge lines for hydraulic fluid and there is a lift control valve unit with a minimum of interfaces.
  • a second aspect of the invention relates to a hydraulic lift system with a lift control valve according to the first aspect of the invention.
  • the lift system has a hydraulic pump connected or connectable to the first connection of the lift control valve, a tank for hydraulic fluid connected or connectable to the second connection of the lift control valve and a hydraulic drive connected or connectable to the third connection of the lift control valve, with which a lift of the lift system is driven can.
  • the hydraulic drive is preferably designed as a linear drive in the form of a hydraulic cylinder, but it may also be designed differently, e.g. as a rotary hydraulic motor.
  • the formation of such a lift system represents a proper use of the lift control valve according to the first aspect of the invention.
  • the lift system has a lift control valve with an arrangement which is equipped with means for determining the opening of the throttle cross section of the throttle arrangement, the relative position of the drive element and / or the relative position of the throttle body of the throttle arrangement.
  • this embodiment of the lift system comprises a control for the driving operation of the lift, which is so connected to the aforementioned means and is configured that they operate via this means information about the opening of the throttle cross-section, the relative position of the drive element and / or the relative position of the throttle body can receive and this can take into account in the control or regulation of the driving operation of a lift of the lift, and preferably as a parameter representing the hydraulic fluid flow which flows through the throttle cross-section of the arrangement, and in particular the associated travel speed of the lift.
  • With such hydraulic lifts it is possible to realize a very precise regulation of the travel speed of the lift with little system outlay.
  • the volume flow of hydraulic fluid delivered through the throttle cross-section of the throttle arrangement is determined by means of an algorithm exclusively from the determined opening of the throttle cross-section, the determined relative position of the drive element and / or the determined relative position of the throttle body of the throttle arrangement, possibly with additional consideration of a additionally determined temperature value of the hydraulic fluid.
  • the volume flow of hydraulic fluid delivered through the throttle cross section of the throttle arrangement is changed by the larger or smaller part of the volume flow conveyed by the hydraulic pump being diverted into the tank by the control unit of the lift control valve. In this way, the use of low-constant pumps is possible and the entire regulation via the lift control valve.
  • Fig. 1 shows a section through an inventive lift control valve in a de-energized rest state of the lift control valve.
  • the lift control valve on a solid metal housing 3, within which by inserting various functional units from the outside a hydraulically actuated 3/4-way main valve 14, an electrically actuated pilot valve 15 for the main valve 14, a pressure relief valve 18, a unlockable check valve 22 and a switching valve 8 are formed for the check valve 22.
  • the check valve 22, together with the switching valve 8, is a claimed arrangement for providing a variable throttle cross section for a hydraulic fluid flow to be controlled by the lift control valve for a hydraulic lift drive.
  • the main valve 14 is designed as a continuously acting slide valve, with a piston slide 17 which limits a control oil chamber 25 at its left end and forms at this end together with a control edge of the housing 3 a variable depending on the spool position throttle body 16.
  • a spring chamber 27 At its right end of the spool 17 limits a spring chamber 27, in which a return spring 26 is arranged, which pushes the spool 17 at unpressurized control oil chamber 25 to the left in a basic position.
  • the spring chamber 27 is limited over a part of its axial extent and at its end facing away from the spool 17 end of a throttle sleeve 28, which relieves pressure on this space 27 via a throttle point formed by them to the second port 12 (tank connection).
  • a central bore 30 is further arranged with a check valve 31, via which oil from a radial groove 32 on the circumference of the spool 17 in the spring chamber 27 can be passed.
  • the pilot valve 15 for controlling the main valve 14 is formed as a steadily acting seat valve, which forms a check valve in the illustrated currentless state in the direction of its intended flow direction.
  • the main valve 14 and the associated pilot valve 15 form the claim as appropriate control unit of the lift control valve.
  • the unlockable check valve 22 is formed in a seated construction, with a in the housing 3 against the force of a spring 23 (the claimed first force) slidable throttle body 2 and a fixedly arranged in the housing 3 valve seat body 9.
  • the throttle body 2 and the valve seat body 9 formed throttle section 1 closed in a basic position with non-deflected throttle body 2 fluid-tight and changeable by deflection of the throttle body 2 from the basic position in dependence on the position of the throttle body 2.
  • the throttle body 2 forms in the present case at the same time the claimed drive element 4 by having axial surfaces which are in direct contact with a claimed first fluid chamber 5, a claim according to the second fluid chamber 6 and a claim according third fluid chamber 7, so that due corresponding second, third and fourth forces in and against the force direction of the spring 23 can be exerted on the throttle body 2 by fluid pressures in these fluid spaces 5, 6, 7. If the sum of these second, third and fourth forces, the force of the spring 23 in the opposite direction, the throttle body 2 is lifted from the valve seat body 9 and the throttle section 1 is opened so far that a balance between the spring force and the sum of the second, third and fourth forces in the direction opposite to the spring force is present.
  • the ratios of the axial areas of the throttle body 2, 4 are selected such that the second, the third and the fourth force with identical fluid pressure in the first, second and third fluid chamber 5, 6, 7 cancel each other.
  • the throttle body 2 is coupled at its right end with a position sensor 10, with which its position in the housing 3 in the form of electrical signals can be determined, to determine the flow during operation through the throttle section 1 of the throttle valve 22 flow of hydraulic fluid.
  • the switching valve 8, which serves as a claim switching arrangement for switching the check valve 22 is formed as a switching 3/2-way valve in slide construction and is located in the in Fig. 1 illustrated situation in a position in which it fluidly connects the second fluid chamber 6 and the third fluid chamber 7 and separates them from the first fluid chamber 5.
  • the throttle cross-section 1 of the check valve 22 can only be opened if a fluid pressure is generated in the first fluid chamber 5, which exceeds the fluid pressure in the second 6 and in the third fluid chamber 7 and additionally is large enough to the force of the spring 23 in the basic position to overcome.
  • the piston valve of the switching valve 8 is loaded by a spring in this way, so that it is held in the position shown in the absence of greater forces acting in the direction opposite to the spring force.
  • This spring is arranged in a spring chamber 24, which is fluidically connected via a throttle point in the piston valve with the second 6 and third fluid chamber 7.
  • the spring chamber 24 is fluidly in contact with the end face of the throttle sleeve 28 of the main valve 14, to which a central pressure relief opening 19 for pressure relief of the spring chamber 24 is located, which in the in Fig. 1 shown operating situation is fluid-tightly closed by a spring-loaded ball, so that the spring chamber 24 is not depressurized in this operating situation.
  • the spool 17 of the main valve 14 has at its right end to an actuating pin 29, by means of which he can open the pressure relief opening 19 by lifting the spring-loaded ball from its seat in a fully controlled position and thereby the spring chamber 24 of the switching valve 8 with the spring chamber 27 of the Main valve 14 can connect fluidly.
  • Fig. 3 shows the hydraulic scheme of a hydraulic lift system formed with this lift control valve
  • the first fluid chamber 5, which is arranged on the claim Demand first side of the throttle section 1 of the check valve 22, via the main valve 14 optionally with a first port 11 for one of A supply line for hydraulic fluid coming from a hydraulic pump 33 can be connected to a second connection 12 for a return of hydraulic fluid into a tank 34.
  • the second fluid space 6, which is arranged on the claimed second side of the throttle cross-section 1 of the check valve 22, is permanently connected to a third connection 13 for a hydraulic line leading to a hydraulic drive 35 of a lift system and to the inlet side of the pilot valve 15.
  • the throttle gap 1 is completely closed, so that the first 5 and the second fluid chamber 6 are fluidly separated from each other via this.
  • the pressure relief valve 18 is located in the feed from the pilot valve 15 for the control oil to the control oil chamber 25 of the main valve 14 and is designed such that when exceeding a certain fluid pressure at the first port 11, this feed is connected to the second port 12 for the tank and thereby the control oil pressure collapses.
  • the throttle body 2 is deflected to the right.
  • the throttle cross-section 1 opens and hydraulic oil flows under pressure from the first port 11 to the third port 13 and from there to the hydraulic lift drive 35, in the present case a one-way hydraulic cylinder.
  • This state corresponds to the OPEN-drive operation of the lift control valve.
  • the position of the throttle body 2 via the sensor 10 as an electrical position signal for an electronic control can be tapped and is available for a determination of the flowing through the throttle cross-section volume flow hydraulic oil, without requiring a determination of pressure values.
  • the changeover valve 8 remains in its ON position during the OPEN-DRIVE operation, since the spring chamber 24 on the right-hand side of its piston valve, which is not relieved of pressure in this operating situation, is in fluid communication with the second fluid chamber 6 and third fluid chamber 7 via a throttle point in the piston valve and whose spring compensates for the slight overpressure in the first fluid space 5 with respect to the pressures in the second 6 and third fluid space 7 or in the spring space 24.
  • the control oil pressure can push the spool 17 of the main valve 14 into the in-port valve 13 Fig. 2 Move shown position to the right, which lifts the spring-loaded ball, which closes the discharge port 19 fluid-tight, with its actuating pin 29 from its seat.
  • the first fluid chamber 5 is connected directly via the main valve 14 and the spring chamber 24 of the changeover valve 8 indirectly via the discharge opening 19 and the throttle sleeve 28 with the second port 12 and the tank 34 and thereby relieved of pressure.
  • the fluid pressure in the second fluid space 6 in conjunction with the axial surfaces of the spool of the switching valve 8, to which it acts, is sufficient to deflect this spool against the spring force to the right.
  • the first fluid space 5 is connected to the third fluid space 7, while the second fluid space 6 is separated therefrom.
  • the fluid pressure in the second fluid chamber 6 which acts axially only on an annular surface of the throttle body 2, in conjunction with the fluid pressure in the first fluid chamber 5, which extends to the end face of the throttle body. 2 acts to move the throttle body 2 from the home position to the right and thereby open the throttle area 1.
  • the hydraulic fluid flows from the second fluid chamber 6 via the throttle cross-section 1 in the first fluid chamber 5 and from there via the main valve 14 and the second port 12 in the tank 34.
  • This state corresponds to the AB drive operation of the lift control valve, said Again, as already in the previously described ON-ride operation, the position of the throttle body 2 via the sensor 10 as an electrical position signal for an electronic control (not shown) can be tapped and so for a determination of the now in the reverse direction through the throttle section. 1 flowing volume flow hydraulic oil is available, again without the need for this purpose, a determination of system pressures.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (22)

  1. Soupape de régulation d'ascenseur avec un arrangement pour prévoir une ajustable section transversale d'étranglement pour un écoulement de fluide, particulièrement pour un écoulement de liquide,
    l'arrangement comprenant
    un arrangement d'étranglement (20) avec une section transversale d'étranglement (1) qui est ajustable par le mouvement d'un corps d'étranglement (2),
    un arrangement d'entrainement (21) avec un élément d'entrainement (4) arrangé de manière déplaçable dans une carcasse (3) et couplé avec le corps d'étranglement (2) de l'arrangement d'étranglement afin d'ajuster la section transversale d'étranglement (1) dépendant de sa position relative dans la carcasse (3),
    l'arrangement étant formé de sorte que l'élément d'entrainement (4) soit permanemment exposé à une première force de ressort ou peut être exposé à une première force de ressort, qui est appliquée à l'élément d'entrainement (4) dans une première direction de sa mobilité et qui positionne l'élément d'entrainement (4) dans une position de base dans la carcasse (3) en absence de forces au moins égales et actionnant sur l'élément d'entrainement (4) dans une deuxième direction opposée à la première direction,
    à cause d'une pression d'un fluide dans un premier espace fluidique (5) de l'arrangement, qui est connecté ou connectable avec une première face de la section transversale d'étranglement, l'élément d'entrainement (4) soit exposé à une deuxième force qui agit dans la deuxième direction,
    à cause d'une pression d'un fluide dans un deuxième espace fluidique (6) de l'arrangement, qui est connecté ou connectable de manière fluidique avec la deuxième face de la section transversale d'étranglement, l'élément d'entrainement (4) soit exposé à une troisième force qui agit dans la deuxième direction,
    à cause d'une pression d'un fluide dans un troisième espace fluidique (7) de l'arrangement, l'élément d'entrainement (4) soit exposé à une quatrième force qui agit dans la première direction,
    de sorte que l'élément d'entrainement (4) soit déplacé de la position de base jusqu'à un équilibre de forces entre la première force de ressort agissant sur l'élément d'entrainement (4) dans la correspondante position relative du même et la force résultante ou une position de déplacement maximal est atteinte, en cas aucune autre force agit dans la première ou la deuxième direction sur l'élément d'entrainement (4) et la somme de la deuxième, troisième et quatrième force est une force résultante qui agit dans la deuxième direction et qui est supérieure à la première force de ressort qui agit sur l'élément d'entrainement dans la première direction dans la position de base,
    et l'arrangement comprenant en outre
    un arrangement de commutation (8) à l'aide duquel sélectivement soit le premier espace fluidique (5) et le troisième espace fluidique (7) sont connectables l'un à l'autre, soit le deuxième espace (6) et le troisième espace fluidique (7),
    la soupape de régulation d'ascenseur ayant un connecteur (11) pour une conduite d'alimentation de liquide hydraulique qui arrive d'une pompe hydraulique, un deuxième connecteur (12) pour une conduite de retour de liquide hydraulique dans un récipient et un troisième connecteur (13) pour un tuyau hydraulique menant à un entrainement hydraulique d'une installation d'ascenseur, ainsi qu'un arrangement de commande (14, 15) formé de sorte que le premier espace fluidique (5) de l'arrangement et la première face de la section transversale d'étranglement (1) soient connectables de manière fluidique sélectivement avec le premier connecteur (11) ou avec le deuxième connecteur (12), et le deuxième espace fluidique (6) de l'arrangement et la deuxième face de la section transversale d'étranglement (1) soient connectés ou connectables avec le troisième connecteur (13).
  2. Soupape de régulation d'ascenseur selon la revendication 1, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que la section transversale d'étranglement (1) de l'arrangement d'étranglement soit entièrement fermée quand l'élément d'entrainement (4) est arrangé dans la position de base.
  3. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable comprenant des moyens pour déterminer l'ouverture de la section transversale d'étranglement (1) de l'arrangement d'étranglement, la position relative de l'élément d'entrainement (4) dans la carcasse (3) et/ou la position relative du corps d'étranglement (2) de l'arrangement d'étranglement, particulièrement des capteurs (10) à l'aide duquels les position relatives de l'élément d'entrainement (4) et/ou du corps d'étranglement (2) sont convertibles en signaux électriques.
  4. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que la deuxième et la troisième force sont essentiellement égales en cas des pressions fluidiques identiques dans le premier espace fluidique (5) et dans le deuxième espace fluidique (6).
  5. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que la deuxième, troisième et quatrième force s'annulent réciproquement essentiellement en cas des pressions fluidiques identiques dans le premier, deuxième et troisième espace fluidique (5, 6, 7).
  6. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que l'élément d'entrainement (4) a des surfaces axiales qui sont connectées de manière fluidique chacune avec le premier, deuxième et troisième espace fluidique (5, 6, 7) afin de générer la deuxième, troisième et quatrième force.
  7. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que l'arrangement d'étranglement est formé comme soupape à siège.
  8. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement pour prévoir la section transversale d'étranglement ajustable étant formé de sorte que l'élément d'entrainement (4) de l'arrangement d'entrainement et le corps d'étranglement (2) de l'arrangement d'étranglement sont formés par un élément commun.
  9. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, la soupape de régulation d'ascenseur étant formée de sorte qu'une connexion du deuxième espace fluidique (6) avec le troisième espace fluidique (7) est automatiquement effectuée par l'arrangement de commutation (8) en opération comme prévu quand le premier espace fluidique (5) avec la première face de la section transversale d'étranglement est connecté avec le premier connecteur (11), et qu'une connexion du premier espace fluidique (5) avec le troisième espace fluidique (7) est automatiquement effectuée par l'arrangement de commutation (8) quand le premier espace fluidique (5) avec la première face de la section transversale d'étranglement est connecté avec le deuxième connecteur (12).
  10. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement de commande (14) pour permettre la connexion sélective de la première face de la section transversale d'étranglement (1) avec le premier connecteur (11) ou avec le deuxième connecteur (12) a une soupape principale (14), particulièrement opérable de manière hydraulique, particulièrement qui agit de manière continue et particulièrement qui est en forme de poussoir à piston.
  11. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, une soupape (18) étant présente, qui connecte l'alimentation de fluide à l'entrainement hydraulique de la soupape principale (14) avec le deuxième connecteur (12) quand une certaine pression au premier connecteur (11) est atteinte.
  12. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, la soupape de régulation d'ascenseur comprenant une vanne pilote (15) opérable électriquement pour la soupape principale (14) opérable de manière hydraulique, à l'aide de laquelle l'entrainement hydraulique de la soupape principale (14) est connectable de manière fluidique ou peut être déconnectée de manière fluidique sélectivement avec la deuxième face de la section transversale d'étranglement (1) et/ou avec le deuxième espace fluidique (6), afin d'opérer la soupape principale (14).
  13. Soupape de régulation d'ascenseur selon la revendication 12, la connexion fluidique entre la vanne pilote (15) et l'entrainement hydraulique de la soupape principale (14) ayant un point d'étranglement (16) menant au deuxième connecteur (12).
  14. Soupape de régulation d'ascenseur selon la revendication 13, le point d'étranglement (16) ayant une section transversale d'étranglement ajustable dépendant de la position de soupape de la soupape principale (14), particulièrement dépendant de la position du poussoir à piston (17) en cas de la construction de la soupape principale en forme de poussoir à piston, la section transversale d'étranglement étant formée, particulièrement en cas de la construction de la soupape principale (14) en forme de poussoir à piston, entre le poussoir à piston (17) de la soupape principale (14) et un élément fixe de la soupape principale (14).
  15. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement de commande (14, 15) étant formé de sorte qu'une connexion de la première face de la section transversale d'étranglement (1) de l'arrangement d'étranglement et/ou du premier espace fluidique (5) avec le deuxième connecteur (12) n'est pas possible quand du liquide hydraulique est sous pression au premier connecteur (11).
  16. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'arrangement de commutation (8) ayant une soupape de commutation (8) opérable de manière hydraulique, qui est commutable en opération comme prévu par une ouverture ou bien une fermeture d'une ouverture de réduction de pression (19) et l'arrangement de commande (14, 15) étant formé de sorte qu'il ouvre l'ouverture de réduction de pression (19) de la soupape de commutation (8) quand la première face de la section transversale d'étranglement (1) de l'arrangement d'étranglement et/ou le premier espace fluidique (5) avec le deuxième connecteur (12) sont connectés.
  17. Soupape de régulation d'ascenseur selon l'une des revendications précédentes, la soupape de régulation d'ascenseur étant formée de sorte que l'énergie d'opération nécessaire pour l'opération de ses soupapes (8, 14) opérables de manière hydraulique soit extraite du liquide hydraulique guidé en opération dans la soupape de régulation d'ascenseur.
  18. Installation d'ascenseur hydraulique avec une soupape de régulation d'ascenseur selon l'une des revendications précédentes, l'installation d'ascenseur ayant une pompe hydraulique (33) connectée ou connectable avec le premier connecteur (11) de la soupape de régulation d'ascenseur, un récipient (34) connecté ou connectable avec le deuxième connecteur (12) de la soupape de régulation d'ascenseur et un entrainement hydraulique (35), particulièrement un cylindre hydraulique, à l'aide duquel un ascenseur de l'installation d'ascenseur peut être entrainé, connecté ou connectable avec le troisième connecteur (13) de la soupape de régulation d'ascenseur.
  19. Installation d'ascenseur hydraulique selon la revendication 18, la soupape de régulation d'ascenseur étant formée avec des moyens (10) pour déterminer l'ouverture de la section transversale d'étranglement (1) de l'arrangement d'étranglement, la position relative de l'élément d'entrainement (4) et/ou la position relative du corps d'étranglement (2) de l'arrangement d'étranglement, et l'installation d'ascenseur comprenant en outre une commande pour l'opération de circulation de l'ascenseur, qui est connectée avec ces moyens (10) et formée de sorte qu'elle puisse recevoir par ces moyens (10) des informations sur l'ouverture de la section transversale d'étranglement (1), la position relative de l'élément d'entrainement (4) et/ou la position relative du corps d'étranglement (2) et qu'elle puisse les prendre en compte pendant la commande ou bien la régulation de l'opération de circulation d'un ascenseur de l'installation d'ascenseur, particulièrement comme paramètre qui représente l'écoulement de liquide hydraulique qui s'écoule à travers la section transversale d'étranglement (1) de l'arrangement d'étranglement, et particulièrement la vitesse de circulation de l'ascenseur.
  20. Procédé d'opération d'une installation d'ascenseur hydraulique selon l'une des revendications 18 à 19, comprenant les étapes
    lever un ascenseur de l'installation d'ascenseur en transportant un volume d'écoulement de liquide hydraulique à partir de la pompe hydraulique (33) à l'entrainement hydraulique (35) de l'ascenseur, le liquide hydraulique de la section transversale d'étranglement (1) de l'arrangement d'étranglement s'écoulant à partir de la première face de la section transversale d'étranglement (1) à la deuxième face de la section transversale d'étranglement (1) et le deuxième espace fluidique (6) et le troisième espace fluidique (7) étant connectés de manière fluidique l'un avec l'autre et avec la deuxième face de la section transversale d'étranglement (1), alors que la première face de la section transversale d'étranglement (1) est connectée de manière fluidique avec le premier espace fluidique (5)
    ou
    baisser un ascenseur de l'installation d'ascenseur en transportant un volume d'écoulement de liquide hydraulique à partir de l'entrainement hydraulique (33) de l'ascenseur dans le récipient (34), le liquide hydraulique s'écoulant à partir de la deuxième face de la section transversale d'étranglement (1) à la première face de la section transversale d'étranglement (1) à travers la section transversale d'étranglement (1) de l'arrangement d'étranglement et le premier espace fluidique (5) et le troisième espace fluidique (7) étant connectés de manière fluidique l'un avec l'autre et avec la première face de la section transversale d'étranglement (1), alors que la deuxième face de la section transversale d'étranglement (1) est connectée de manière fluidique avec le deuxième espace fluidique (6);
    déterminer l'ouverture de la section transversale d'étranglement (1) de l'arrangement d'étranglement, la position relative de l'élément d'entrainement (4) de l'arrangement d'entrainement et/ou la position relative du corps d'étranglement (2) de l'arrangement d'entrainement pendant le transport du volume d'écoulement de liquide hydraulique à travers la section transversale d'étranglement;
    comparer l'ouverture de la section transversale d'étranglement (1) déterminée, la position relative de l'élément d'entrainement (4) déterminée, la position relative du corps d'étranglement (2) de l'arrangement d'entrainement déterminée et/ou une valeur déduite d'une ou plusieurs de ces variables déterminées avec une valeur de consigne; et
    ajuster le volume d'écoulement du liquide hydraulique transporté à travers la section transversale d'étranglement (1) si une déviation de la valeur de consigne est détectée, de sorte que l'ouverture de la section transversale d'étranglement (1), la position relative de l'élément d'entrainement (4), la position relative du corps d'étranglement (2) et/ou la valeur déduite s'approchent à la valeur de consigne.
  21. Procédé selon la revendication 20, quand l'ascenseur est levé, le volume d'écoulement de liquide hydraulique qui est transporté à travers la section transversale d'étranglement (1) de l'arrangement d'entrainement étant ajusté en déviant une quantité plus ou moins importante du volume d'écoulement de liquide hydraulique transporté à l'aide de la pompe hydraulique (33) dans le récipient (34) à l'aide de l'unité de commande (14, 15) de la soupape de régulation d'ascenseur.
  22. Procédé selon l'une des revendications 20 à 21, le volume d'écoulement de liquide hydraulique qui est transporté à travers la section transversale d'étranglement (1) étant déterminé à l'aide d'un algorithme uniquement sur la base de l'ouverture de la section transversale d'étranglement (1) déterminée, la position relative de l'élément d'entrainement (4) déterminée, la position relative du corps d'étranglement (2) de l'arrangement d'entrainement déterminée, éventuellement en prenant en considération une valeur de température du liquide hydraulique également déterminée.
EP09775737.1A 2009-07-06 2009-07-06 Dispositif constituant une restriction variable pour un écoulement fluidique Active EP2452078B1 (fr)

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WO2016197252A1 (fr) * 2015-06-12 2016-12-15 Westport Power Inc. Système de commande de fluide à haute pression et procédé de commande de modification de pression dans un dispositif d'utilisation finale
CN105807793A (zh) * 2016-05-24 2016-07-27 中冶焦耐工程技术有限公司 一种除尘管道尘气流量调整***
CN114033652B (zh) * 2021-11-24 2023-03-24 中国石油化工股份有限公司 煤气化用高压煤浆泵的补排油阀的阀芯升程的调整方法

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DK151077C (da) 1974-10-11 1988-04-05 Dansk Ind Syndikat Fluidumstyret ventil
US4202174A (en) * 1978-05-16 1980-05-13 Bocharov Jury A Hydraulic drive
DE2928737A1 (de) * 1979-07-17 1981-01-29 Sack Gmbh Hydraulische steuerung mit rohrbruchsicherung fuer einen doppelt beaufschlagbaren antriebszylinder zum positionieren, insbesondere einer angetriebenen fuehrungsrolle in der strangfuehrung einer stranggiessanlage
JPH01133503U (fr) * 1988-03-03 1989-09-12
JP3505869B2 (ja) * 1995-09-14 2004-03-15 株式会社島津製作所 流体制御弁
US5937645A (en) * 1996-01-08 1999-08-17 Nachi-Fujikoshi Corp. Hydraulic device
JP3556860B2 (ja) * 1999-05-28 2004-08-25 新キャタピラー三菱株式会社 流体圧アクチュエータ制御装置
DE10310314B4 (de) * 2003-03-10 2006-04-27 Sauer-Danfoss Aps Antriebsanordnung, insbesondere Hebevorrichtung eines Arbeitsfahrzeugs

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CN102483077B (zh) 2015-11-25
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US20120125190A1 (en) 2012-05-24
US9032861B2 (en) 2015-05-19

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